Torsion isolator spring with pivotal ends

ABSTRACT

A torsion isolator (34) for transmitting torque and dampening torsionals in a driveline. The isolator includes a composite c-shaped spring (48) disposed in an annular chamber (44) of a housing (38,40) filled with torque converter fluid. The spring transmits driveline torque and attenuates torsionals. The spring also functions as a fluid displacement piston by dividing the chamber into radially inner and outer volumes (44a,44b) which vary inversely in volume in response to torque changes flexing the spring. Rapid flexing of the spring increases the fluid pressure in the decreasing volume and thereby dampens or reduces the rate of spring flexing or rebound.

CROSS-REFERENCE

This application is related to U.S. applications, Ser. Nos. 08/236,809,08/236,835 and 08/236,838, filed on May 2, 1995.

FIELD OF THE INVENTION

This invention relates to torsion isolator. More specifically, theinvention relates to an isolator for attenuating and dampening vehicledriveline torsional.

BACKGROUND OF THE INVENTION

It is well known that the speed of an Otto or Diesel cycle engine outputor crankshaft varies even during so-called steady-state operation of theengine, i.e., the shaft continuously accelerates and decelerates aboutthe average speed of the shaft. The accelerations and decelerations are,of course for the most part, a result of power pulses from the enginecylinders. The pulses may be of uniform frequency and amplitude whencylinder charge density, air/fuel ratio and ignition are uniform.However, such uniformity does not always occur, thereby producing pulseswhich vary substantially in frequency and amplitude. Whether uniform ornot, the pulses, which are herein referred to as torsionals, aretransmitted through vehicle drivelines and are perceptible to vehiclepassengers. The torsionals, which manifest themselves as vibrations aredetrimental to drivelines, derogate passenger-ride quality, and maycause annoying body noises. An example of body noise, known as bodyboom, occurs when an engine is lugged; under such a condition enginetorsionals may cause body components, such as sheet metal panels, toresonate. Still further, tip-in/tip-out torque pulses, produced byabrupt engine acceleration and/or deceleration, jerk the driveline andvehicle; such torque pulses are also referred to herein as torsionals.

Torsion isolators for attenuating and dampening driveline torsionals arewell known in the prior art. Such isolators commonly employ a spring(s)and a damper. The spring(s) attenuate the torsionals and transmitpositive and negative torque (i.e., engine and coast torque) between thevehicle engine and wheels. The damper controls the rate of springflexing. Examples of such isolators may be seen by reference to U.S.Pat. Nos. 5,240,457; 5,234,377; 4,782,932 and published French patentapplication 2,611,013. These documents are incorporated herein byreference. The torsion isolator disclosed herein is considered to haveseveral advantages over the above torsion isolators with respect totorsional attenuation and damping, cost, and weight or inertia.

SUMMARY OF THE INVENTION

An object of the invention is to provide an improved torsion isolator.

According to a feature of this invention, a torsion isolator, such asdisclosed in U.S. Pat. No. 5,234,377, includes first and second drivesmounted for relative rotation about a common axis. A c-shaped spring hasa flexible major arc portion circumscribing the axis and has first andsecond circumferentially spaced apart ends. Attachment means connect thefirst and second ends respectively to the first and second drives at aradial distance from the axis. The spring transmits torque between thedrives and attenuates torsionals. The spring ends are circumferentiallymovable relative to each other in response to changing values of thetorque and torsionals.

The improvement is characterized by the spring first and second endsrespectively including first and second brackets rigidly affixedthereto. Pivot means pivotally connect the first and second bracketsrespectively to the first and second drives. Stop means are operative inresponse to a predetermined amount of pivotal movement of the bracketsto stop further pivotal movement.

BRIEF DESCRIPTION OF THE DRAWINGS

The torsion isolator of the present invention is shown in theaccompanying drawinging which:

FIG. 1 is a schematic view of a motor vehicle driveline;

FIG. 2 is a detailed, sectional view of the torsion isolator disposed ina partially shown torque converter housing and looking along line 2--2of FIG. 3;

FIG. 3 is a relief view of the torsion isolator of FIG. 2 with a housingmember removed and looking in the direction of arrow 3 in FIG. 2;

FIG. 4 is a sectional view of the torsion isolator looking along line4--4 of FIG. 3;

FIG. 5 is a relief view similar to FIG. 3 with a spring therein shownfully stressed in one direction;

FIG. 6 is an exploded view of the torsion isolator;

FIG. 7 is a sectioned half view of a second embodiment of the torsionisolator;

FIG. 8 is an enlarged schematic view of a portion of a composite springillustrating layers of reinforcing filaments protruding from a matrix ofplastic material;

FIGS. 9--11 illustrate an active counterbalance mechanism for thetorsion isolator of FIG. 2-6;

FIGS. 12 and 13 illustrate slack mechanism for the isolator of FIGS.2-6; and

FIG. 14 illustrates an alterative slack mechanism embodiment.

DETAILED DESCRIPTION OF THE DRAWINGS

The motor vehicle driveline seen schematically in FIG. 1 includes aninternal combustion engine 10, an automatic transmission 12 and a driveshaft 14 driving a load such as rear and/or front wheels 16 of a vehiclethrough a differential 18.

The transmission includes a torque converter assembly 20 having anoutput shaft 22 rotatable about an axis 22a (FIG. 2) and a gear ratiobox 24 driven by the torque converter output shaft 22. Torque converterassembly 20 is filled with automatic transmission fluid and includes, ina known manner, an impeller 26 driven by engine 10 through a torqueconverter housing 28, a stator 30, and a turbine 32 drivenhydrokinetically by the impeller. A fluid coupling may be employed inlieu of a torque converter.

Torque converter assembly 20 further includes the torsion isolator 34 ofthe present invention disposed to selectively bypass the torqueconverter impeller in response to pressurized torque converter fluidhydraulically moving the torsion isolator axially into frictionalengagement with the torque converter housing 28 by a friction material35 in known manner. During non-bypass operation of the torque converter,the pressurized torque converter fluid is admitted to the torqueconverter via a chamber 36 receiving the fluid through unshown passagesin shaft 22 in known manner. The fluid in chamber 36 prevents frictionalengagement of the isolator housing with the torque converter housing.The fluid in chamber 36 flows radially outward and into the torqueconverter in a main torque converter chamber 37 separated from chamber36 by isolator 34. When it is desired to engage the isolator, as forexample, when the vehicle is in motion, the direction of flow of thepressurized fluid is reversed by actuation of a suitable valve, notshown. Specifically, the pressurized fluid is now admitted to chamber 37where it acts against the radially extending portion of the isolatorfacing chamber 37 and slides the entire isolator to the right to effectfrictional engagement with the torque converter housing. Drivelinetorque now bypasses the torque converter and is transmitted to shaft 22by the isolator.

Referring now to FIGS. 2-6, torsion isolator 34 comprises housingmembers 38,40 and an annular ring 42 defining an annular chamber 44, ahub 46, and a c-shaped spring 48. Housing member 38 includes a radiallyextending portion 38a having a surface 38b defining an axially facingsurface of chamber 44, a radially outer and axially extending portion38c having a cylindrical surface 38d defining a radially outer surfaceof the chamber, and a radially inner and axially extending portion 38econcentric to axis 22a when mounted for relative sliding and rotationalmovement on an end of shaft 22. Oil leakage flow between the interfaceof shaft 22 and housing portion 38e is prevented by an o-ring seal 50.

Hub 46 includes a radially inner and axially extending portion 46arotatably supported on housing portion 38e by a needle bearing 52, aplurality of circumferentially spaced apart holes 46b slidably receivingextensions of fasteners 53 drivingly securing turbine 32 to shaft 22,axially oppositely facing annular surfaces 46c,46d, and an arm 46eextending radially outward from annular surfaces 46c,46d and intoannular chamber 44. Surface 46d is disposed for sliding sealing relationwith a radially inner portion of housing surface 38b.

Annular ring 42 includes an arcuate opening or recess 42a having hub arm46e extending therethrough, end surfaces 42b,42c defining the arcuatelength of the recess, an axially facing annular surface 42d disposed forsliding sealing relation with hub surface 46c, an inner circumference42e concentric to hub portion 46a, an elliptical or irregular outercircumferential surface 42f explained further hereinafter, axiallyspaced apart surfaces 42g,42h, an annular shoulder or ridge 42i, andthree substantially equally spaced apart recesses 42j in shoulder 42i.

C-shaped spring 48 is preferably, but not necessarily formed of acomposite material including layers of reinforcing filaments 47encapsulated in a matrix of plastic material 49 in known manner. SeeFIG. 8. Further details of such springs may be obtained by reference toU.S. Pat. Nos. 5,219,431 and 5,234,377, which are incorporated herein byreference, or from A. O. Smith Corporation, Milwaukee, Wis., U.S.A.Spring 48 includes circumferentially spaced apart and aligned ends48a,48b and a bracket 54 affixed to each end. The brackets may beaffixed to the spring ends in any of several known manners. Hereinscrews 56 are used. A radially inner portion of each bracket has anaxial thickness less than the axial thickness of spring 48 and a slot54a. The bracket affixed to spring end 48a loosely receives hub arm 46ein slot 54a with axial free play and is pivotally connected thereto by apin 58 extending through openings in the bracket and arm. The bracketaffixed to spring end 48b is pivotally connected to housing members38,40 by a pin 60 extending through openings in the bracket and housingmembers. The bracket affixed to spring end 48b need not include slot54a. A radially outer portion of each bracket has axially oppositelyfacing surfaces 54b,54c flush with axially oppositely facing surfaces48c,48d of spring 48, a radially outwardly facing surface 54d having aradius of curvature complementary to and in sliding sealing relationwith housing member surface 38d, and an edge 54e of each surface 54d hasa reduced radius concentric to pins 58,60 so as to allow pivotalmovement of the brackets and maintain the sliding sealing relation withthe housing surface 38d.

Radial positioning of housing member 40 relative to housing member 38and annular ring 42 is provided by outer and inner circumferentialsurfaces 40a, 40b of housing member 40, which are snugly receivedrespectively by housing surface 38d and ring annular shoulder 42i. Axialpositioning of an axially facing surface 40c of housing member 40relative to housing surface 38b to provide desired clearance with springsurfaces 48c,48d may be determined solely by dimensional control of thedistance between annular ring surfaces 42g,42h relative to the distancebetween spring surfaces 48c,48d. Alternatively, the cost of dimensionalcontrol may be mitigated by positioning radially extending assemblyshims (not shown) between surfaces 40c,48c of the housing and spring.The shims may be inserted through annular ring recesses 42j and removedafter housing outer circumferential surface 40a is sealingly affixed,for example by welding, to housing surface 38d. Thereafter housingmember 40 is affixed at a radially inner portion thereof to annular ring42 and housing member 38 by fasteners such as rivets 62.

Isolator 34, when installed, is intended to rotate in one direction asindicated by arrow A in FIGS. 3 and 5. Direction A is taken as thedirection of positive torque, i.e., when torque is from the engine tothe wheels. Torque in the opposite direction is taken as negative orcoast mode torque which is produced when drive is from the wheels to theengine. Positive torque moves the spring ends circumferentially towardeach other and decreases the spring radius. Negative torque moves thespring ends circumferentially apart and increases the spring radius.Maximum flex of spring 48 in the positive and negative directions fromthe neutral or unflexed position of FIG. 3 may be limited to any ofseveral predetermined amounts. Herein, maximum flex in the positivetorque direction is limited to about forty-five rotational degrees bycontact of bracket end surfaces or stops 54f, as seen in FIG. 5. Maximumflex in the negative torque direction is limited to about fifteendegrees. Flex in the negative torque direction may be limited in any ofseveral ways, for example, by hub arm 46e contact with annular ringrecess end surface 42c, by contact of the spring outer circumferencewith housing surface 38d, etc.

The rate of spring 48 may be varied by allowing brackets 54 to pivot ornot pivot about pins 58,60 while the spring is flexing. When arelatively low rate is desired, for example, when driving torque is low,pivotal movement may be allowed and then prevented at some highertorque. Herein, by way of example, brackets 54 are allowed to pivotduring the first ten degrees of spring flexing in the positive directionfrom the neutral position. Pivotal movement of the bracket affixed tospring end 48a is arrested or stopped when a bracket surface 54gcontacts a surface 46f of hub arm 46e. Pivotal movement of the bracketaffixed to spring end 48b is arrested or stopped when bracket surface54g contacts the outer surface 42e of annular ring 42.

The flexing of spring 48, as thus far described, has had to do only withrespect to torque transmission and torsional attenuation functions ofthe spring. Spring 48 also functions as a fluid displacement piston bydividing chamber 44 into radially inner and outer volumes 44a,44b whichvary inversely in volume in response to torque changes flexing thespring. The volumes are filled with torque converter fluid, are inrestricted fluid communication with each other by the sealing relationbetween the spring and bracket surfaces and the housing surfaces, andare in restricted fluid communication with the surrounding pressurizedfluid in the torque converter by the less than tight sealing relationbetween surfaces 38b,46d and 46c,42d to ensure full charge of thevolumes. Rapid flexing of the spring increases the fluid pressure in thedecreasing volume and thereby dampens or reduces the rate of springflexing or rebound. Accordingly, housing 38,40, hub 46, spring 48 andthe fluid define a fluid dampening mechanism. As may be seen byreference to FIG. 5, the elliptical or irregular surface 42e of annularring is to allow full positive flexing of spring 48 without contact ofthe spring central portion 48e therewith.

The torsion isolator, as thus far described, is charged by and refilledby the pressurized fluid in the torque converter housing. Alternatively,the isolator may be better sealed as in partially shown torsion isolator70 in FIG. 7. Isolator 70 has a modified, two piece annular ring 72,74and hub 76 to accommodate dynamic seals 78,80. The fluid within theisolator may be other than torque converter fluid, for example, siliconeoil. Further, isolator 70 may be employed in a free standing masterclutch plate commonly used in non-torque converter transmissions or asan inline isolator in any type of driveline. Still further, edges ofspring 48 and brackets 54 may be provided with chambers or bevels 48f topromote generation of a hydrodynamic fluid film between spring andbracket surfaces 48c,48d,54b,54c and housing surfaces 38b,40c forreducing friction and wear therebetween.

Rotational balance of isolator 34 is subject to change sinceconcentricity of spring 48 relative to shaft axis 22a changes as itflexes. The changing balance may be cancelled by use of, for example,two or more springs disposed in separate chambers and circumferentiallypositioned about axis 22a such that the collective balance of thesprings does not change as they flex. Herein, the change in balance is arelatively small amount since the spring is disposed in a closed chamberfilled with a fluid whose density is relatively close to the density ofthe composite material of the spring. However, the change in balancewould be greater if the spring were formed of a denser material such assteel, or if a single spring 48 were used in lieu of the spiral springsin U.S. Pat. No. 5,240,457, on in combination with the viscous fluiddamper in U.S. Pat. No. 4,936,434 incorporated herein by reference.

Isolator 34 may also include some type of dynamic or activecounterbalance mechanism to counter out of balance conditions caused byflexing of spring 48. Herein, brackets 54 function as activecounterbalance mechanisms since they pivot radially inward in responseto positive flexing of the spring from the neutral position of FIG. 3 tothe fully flexed position of FIG. 5.

FIGS. 9-11 illustrate a torsion isolator 90 modified to include anactive counterbalance mechanism 92 which may be used in lieu of or inaddition to the counterbalance provided by pivoting spring brackets 54.Mechanism 92 includes a counterweight 94 disposed for radial movement inan elongated window 96a of a modified hub 96 in response to flexing ofspring 48 allowing rotational movement of the hub relative to a ring 98affixed to a housing member 100 in a manner analogous to the way rings42 and 74 are affixed. Transmission of the radial movement is effectedby a follower 94a of the weight projecting into a cam slot 98a in ring98. As spring 48 flexes in the positive direction, slot 98a pulls weight94 radially inward. As spring 48 flexes in the negative direction, theslot allows the weight to move radially outward. Mechanism 90 or anequivalent thereof may be disposed in any of several places in or on thetorsional isolator. For example, mechanism 90 may be disposeddiametrically opposite the shown position provided cam slot 98a ispositioned to move the weight radially outward in response to increasingpositive flex of the spring and radially inward in response toincreasing negative flex. Further, cam slot 98a may have a curvedprofile in lieu of the linear profile shown so as to provide nonlinearmovement of the weight in response to spring flex.

Isolator 34 may also be provided with a lost dampening mechanism forreducing or negating dampening of low amplitude torsionals since theeffects of such torsionals are readily attenuated or masked by a longtravel spring such as spring 48 without dissipation of the torsionalenergy by the damper. By way of example, the lost dampening mechanismmay have an operative range of one or two rotational degrees on eitherside of a current steady state or average torque. The lost dampening maybe provided by a lost motion mechanism such as disclosed in U.S. Pat.No. 4,608,883, which is incorporated herein by reference. However, themechanism is preferably a hydraulic slack mechanism, two of suchmechanisms are disclosed herein.

Referring now to FIGS. 12 and 13, therein is illustrated a firsthydraulic slack mechanism 110 for allowing momentary flow of torqueconverter fluid from one of the radially inner or outer volumes 44a,44bto the other and thereby slow or delay pressure rise in one volume andfall in the other in response to torsionals as they tend to decrease thesize of one volume and increase the size of the other volume. The amountof fluid flow allowed by mechanism 110, of course, determines the amountof slack or non-hydraulic dampening of spring flexing.

Mechanism 110 is incorporated into a spring bracket 112 which isotherwise the same as bracket 54 and which replaces one or both ofbrackets 54 in isolator 34. Mechanism 110 includes a circumferentiallyextending groove 114 formed in the radially outer surface 112a of thebracket and a circumferentially movable valving member 116 disposed inthe groove. Groove 114 includes a groove portion 114a circumferentiallybounded at its opposite ends by shoulders 114b,114c formed by radiallydeeper groove portions 114d, 114e. The valving member includes, relativeto axis 22a, axially oppositely facing sides 116a, 116b in close slidingrelation to the axially facing sides of the groove, a circumferentiallyextending portion 116c having radially inwardly extending ends 116d,116e respectively received by groove portions 114d, 114e and movableinto sealing relation with shoulders 114b, 114c. When valving memberends 116d, 116e are spaced from shoulder 114b, 114c, torque converterfluid can flow between the volumes 44a, 44b. As pressure rises in onevolume and falls in the other, the differential pressure created therebyacts on valving member ends 116d, 116e and shuttles the valving memberaway from the rising pressure and seals the appropriate ends 116d,116eagainst the corresponding shoulders 114b, 114c. The amount of fluid thatflows during the shuttle period determines the slack or non-hydraulicdampening of the spring flex.

To provide the desired amount of slack or non-dampening in someapplications, a low force spring or springs, not shown, may be employedto position valving member 116 in the neutral position shown, therebyincreasing the amount of differential pressure for shuttling the valvingmember. Further, if or when both of the spring brackets are providedwith valving member 116, one of the valving members may be biased by anunshown low force spring toward shoulder 114b thereby preventing flowfrom volume 44b to volume 44a and the other biased by an unshown lowforce spring toward shoulder 114c thereby preventing flow from volume44a to volume 44b. This arrangement is believed to provide more precisevalve control.

Referring now to FIG. 14, therein is illustrated a lower half ofisolator 34 having a pair of second hydraulic slack mechanisms 120,122for respectively allowing momentarily expansion of volumes 44a, 44b asthey initially start to decrease in size due to flexing of spring 48.Mechanism 120 includes an expansion compartment 124 defined by acup-like member 126 affixed to wall 40 in any of several known manners,through passages 128, 130 in wall 40 and member 126, and a floatingpiston or valving member 132 movable in compartment 124 betweenpositions blocking one of the passages and unblocking the other passage.The structure and operation of mechanism 122 is basically the same asmechanism 120 and therefore is not described further.

When isolator 34 is in operation, volumes 44a,44b are alternatelytending to decrease and increase in size in response to rather smalltorsionals caused by normal engine cylinder power pulses. Hence, atorsional that is currently now, for example, tending to decrease thesize of volume 44a and increase the size of volume 44b was preceded by atorsional that had done the opposite. Accordingly, the pressure inchamber 44a is low relative to torque converter pressure surrounding theisolator and valving member 132 is sealingly seated over passage 130 asthe current oncoming torsional begins. As volume 44a decreases in sizedue to the oncoming torsional, the pressure in volume 44a exceeds torqueconverter pressure, thereby moving valving member 132 to a positionseated over passage 128 and allowing the size of volume 44a to increaseby the size of compartment 124. An unshown low force spring may be usedto bias valving member 132 over passage 130 and the correspondingvalving member over the passage to chamber 44b in mechanism 122.

The appended claims are intended to cover the disclosed embodiments ofthe present invention and modification thereof believed to be within thespirit and scope of the invention.

What is claimed is:
 1. A torsion isolator including first and seconddrives mounted for relative rotation about a common axis; a c-shapedspring having a flexible major arc portion thereof circumscribing theaxis and having first and second circumferentially spaced apart ends;attachment means for connection the first and second ends respectivelyto the first and second drives a radial distance from the axis; thespring for transmitting torque between the drives and for attenuatingtorsionals; the spring ends circumferentially movable relative to eachother in response to changing values of the torque; and means forlimiting maximum relative circumferential movement of the spring endstoward each other; characterized by;the spring first and second endsrespectively including first and second brackets rigidly affixedthereto; pivot means pivotally connecting the first and second bracketsrespectively to the first and second drives; and stop means operative inresponse to a predetermined amount of pivotal movement of the bracketseffected by less than the maximum circumferential movement of the springends toward each other to stop further pivotal movement.
 2. The isolatorof claim 1, wherein:the spring is a composite spring formed by aplurality of reinforcing filaments bonded together by a plasticmaterial.
 3. The isolator of claim 1, further including a dampeningmechanism for reducing the rate of flexing of the major arc in responseto the relative circumferential movement of the spring ends.
 4. Themechanism of claim 3, wherein:the dampening mechanism is a fluiddampener mechanism.
 5. The isolator of claim 4, wherein:the spring is acomposite spring formed by a plurality of reinforcing filaments bondedtogether by a plastic material.
 6. The isolator of claim 1, wherein:thepivot means includes a first pin received in an opening in a radiallyinward portion of the first bracket and in the first drive, and a secondpin received in an opening in a radially inward portion of the secondbracket and in the second drive.
 7. The isolator of claim 6, wherein:thestop means includes a radially outwardly and a radially inwardly facingsurface respectively rigid with one of the drives and the bracketaffixed to the one drive and the surfaces operative to engage inresponse to the predetermined pivotal movement for stopping the pivotalmovement of the bracket relative to the one drive.
 8. The isolator ofclaim 7, wherein:the spring is a composite spring formed by a pluralityof reinforcing filaments bonded together by a plastic material.